US20150240965A1 - Actuator apparatus with internal tubing and anti-rotation mechanism - Google Patents
Actuator apparatus with internal tubing and anti-rotation mechanism Download PDFInfo
- Publication number
- US20150240965A1 US20150240965A1 US14/189,627 US201414189627A US2015240965A1 US 20150240965 A1 US20150240965 A1 US 20150240965A1 US 201414189627 A US201414189627 A US 201414189627A US 2015240965 A1 US2015240965 A1 US 2015240965A1
- Authority
- US
- United States
- Prior art keywords
- pressure chamber
- diaphragm plate
- fluid
- actuator
- tube
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000007246 mechanism Effects 0.000 title description 8
- 239000012530 fluid Substances 0.000 claims abstract description 135
- 238000004891 communication Methods 0.000 claims abstract description 16
- 238000010168 coupling process Methods 0.000 claims description 15
- 230000008878 coupling Effects 0.000 claims description 14
- 238000005859 coupling reaction Methods 0.000 claims description 14
- 238000007789 sealing Methods 0.000 claims 1
- 239000000463 material Substances 0.000 description 7
- 238000000034 method Methods 0.000 description 7
- 238000013022 venting Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000008439 repair process Effects 0.000 description 4
- 230000007613 environmental effect Effects 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000007726 management method Methods 0.000 description 2
- 229920000642 polymer Polymers 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 229910001335 Galvanized steel Inorganic materials 0.000 description 1
- 238000012369 In process control Methods 0.000 description 1
- 239000004677 Nylon Substances 0.000 description 1
- -1 PVC or ABS) Chemical compound 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000008397 galvanized steel Substances 0.000 description 1
- 238000010965 in-process control Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 229920001778 nylon Polymers 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000003252 repetitive effect Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 238000012549 training Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/1226—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston the fluid circulating through the piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/126—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like
- F16K31/1262—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like one side of the diaphragm being spring loaded
- F16K31/1264—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like one side of the diaphragm being spring loaded with means to allow the side on which the springs are positioned to be altered
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/126—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/16—Actuating devices; Operating means; Releasing devices actuated by fluid with a mechanism, other than pulling-or pushing-rod, between fluid motor and closure member
- F16K31/163—Actuating devices; Operating means; Releasing devices actuated by fluid with a mechanism, other than pulling-or pushing-rod, between fluid motor and closure member the fluid acting on a piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/08—Guiding yokes for spindles; Means for closing housings; Dust caps, e.g. for tyre valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/126—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like
- F16K31/1262—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like one side of the diaphragm being spring loaded
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K39/00—Devices for relieving the pressure on the sealing faces
Definitions
- This patent relates generally to actuators and, more particularly, to actuator apparatus having internal tubing and anti-rotation features.
- a fluid control valve assembly typically includes an actuator operatively coupled to a flow control member (e.g., a valve gate, a plug, a closure member, etc.) of a fluid valve.
- the actuator controls the position of the flow control member with respect to a valve seat to control or regulate fluid flow through the valve.
- a controller e.g., a positioner
- a control fluid e.g., air
- a load apparatus e.g., a diaphragm
- a yoke is employed to couple the actuator to the fluid valve.
- the controller is mounted to the yoke.
- Known fluid control valves often employ external tubing to fluidly couple a control fluid between the controller and a chamber (e.g., a pressure chamber) of the actuator.
- a chamber e.g., a pressure chamber
- the external tubing may become damaged or dislodged, thereby affecting the accuracy of the actuator and, thus, a desired fluid flow through the valve.
- fluid flowing through a valve body can impart torsional loads on the flow control member, which can be transmitted to the actuator.
- torsional loads can damage valve seating surfaces and/or internal actuator components, thereby affecting the accuracy of the actuator and, thus, a desired fluid flow through the valve.
- An example apparatus includes an actuator casing and a diaphragm plate disposed within the actuator casing.
- the diaphragm plate defines a first pressure chamber and a second pressure chamber opposite the first pressure chamber.
- a yoke couples the actuator casing to a fluid valve.
- the yoke includes a first internal fluid passageway in fluid communication with atmosphere and a second internal fluid passageway to receive a control fluid from a controller.
- a tube fluidly couples the first or second internal fluid passageway to the first pressure chamber via an opening in the diaphragm plate. The tube also prevents the diaphragm plate from rotating relative to the actuator casing.
- Another example apparatus includes a diaphragm plate disposed within an actuator casing and defining first and second pressure chambers.
- a yoke is coupled to the actuator casing and has first and second fluid passageways.
- a tube fluidly couples the first pressure chamber to one of the first and second fluid passageways in the yoke. The tube extends through an opening in the diaphragm plate to prevent the diaphragm plate from rotating relative to the actuator casing.
- Another example apparatus includes means for actuating a fluid valve and means for attaching the means for actuating to the fluid valve.
- the example apparatus also includes first means for fluidly coupling a first pressure chamber of the means for actuating to atmosphere. A portion of the first means for fluidly coupling is integrally formed with the means for attaching.
- the example apparatus includes second means for fluidly coupling a second pressure chamber of the means for actuating to a control fluid without the use of external tubing. A portion of the second means for fluidly coupling is integrally formed with the means for attaching.
- the first or second means for fluidly coupling further includes means for preventing a valve stem of the fluid valve from rotating relative to the fluid valve.
- FIG. 1A illustrates a known fluid control valve assembly having external tubing.
- FIG. 1B illustrates a partial cross-sectional view of an actuator and yoke of the known fluid control valve of FIG. 1A .
- FIG. 2 illustrates a known actuator apparatus with an anti-rotation feature.
- FIG. 3A illustrates an example direct-acting actuator apparatus with internal tubing and an anti-rotation mechanism.
- FIG. 3B illustrates a detail view of the example direct-acting actuator apparatus of FIG. 3A .
- FIG. 4A illustrates an example reverse-acting actuator apparatus with internal tubing and an anti-rotation mechanism.
- FIG. 4B illustrates a detail view of the example reverse-acting actuator apparatus of FIG. 4A .
- FIG. 5A illustrates an example direct-acting actuator apparatus with internal tubing, an anti-rotation mechanism and a unitary diaphragm plate.
- FIG. 5B illustrates a detail view of the example direct-acting actuator apparatus of FIG. 5A .
- FIG. 6A illustrates an example reverse-acting actuator apparatus with internal tubing, an anti-rotation mechanism and a unitary diaphragm plate.
- FIG. 6B illustrates a detail view of the example reverse-acting actuator apparatus of FIG. 6A .
- FIG. 7 illustrates an example direct-acting actuator apparatus having a non-adjustable bench set.
- FIG. 8 illustrates an example direct-acting actuator apparatus having an adjustable bench set.
- FIG. 9 illustrates an example direct-acting actuator apparatus having an adjustable bench set and a double diaphragm.
- FIG. 10 illustrates an example reverse-acting actuator apparatus having a non-adjustable bench set.
- FIG. 11 illustrates an example reverse-acting actuator apparatus having an adjustable bench set.
- FIG. 12 illustrates an example reverse-acting actuator apparatus having an adjustable bench set and a double diaphragm.
- Example actuator apparatus disclosed herein eliminate the need for external tubing to fluidly couple a control fluid supply (via, e.g., a controller or a positioner) to a chamber (e.g., a pressure chamber) of a fluid valve actuator for both direct-acting and reverse-acting actuator configurations.
- example actuator apparatus disclosed herein include an anti-rotation apparatus to prevent a valve stem from rotating with respect to a valve.
- example apparatus disclosed herein provide venting through a yoke coupled to the actuator.
- Valve actuators are typically available in direct-acting and reverse-acting configurations.
- increasing the pressure of a control fluid (e.g., air) supplied to the actuator pushes the diaphragm down, thereby extending the actuator stem.
- increasing the pressure of a control fluid supplied to the actuator pushes the diaphragm up, thereby retracting the actuator stem.
- Direct-acting actuators are often referred to as air-to-close actuators because increasing air pressure to the actuator extends the actuator stem, which causes the flow control member to move towards the valve seat, thereby restricting fluid flow.
- certain actuators are configured such that extending the actuator stem causes the flow control member to move away from the valve seat, thereby enabling fluid flow.
- reverse-acting actuators are often referred to as air-to-open actuators because increasing air pressure to the actuator retracts the actuator stem, which causes the flow control member to move away from the valve seat, thereby enabling fluid flow.
- certain actuators are configured such that retracting the actuator stem causes the flow control member to move towards the valve seat, thereby restricting fluid flow.
- example actuator apparatus are described in which direct-acting actuators are air-to-close actuators and reverse-acting actuators are air-to-open actuators.
- the present disclosure is also applicable to actuators in which direct-acting actuators are air-to-open actuators and reverse-acting actuators are air-to-close actuators.
- control fluid employed by actuators in accordance with the present disclosure need not be air.
- example actuator apparatus are described as diaphragm actuators.
- present disclosure is also applicable to other types of actuator apparatus, such as piston actuators.
- Example actuator apparatus disclosed herein include a yoke with internal fluid passageways.
- an internal tube or tubing may fluidly couple a first pressure chamber of the actuator with one of first and second internal fluid passageways of the yoke via an opening in a diaphragm plate.
- the internal tubing is rigid and also prevents the diaphragm from rotating, thereby preventing the valve trim from rotating due to torsional forces imparted by fluid flowing through the valve body.
- the internal tube or tubing is fluidly coupled to the second internal fluid passageway of the yoke to supply control fluid to the first pressure chamber.
- the second pressure chamber is in fluid communication with atmosphere via the first internal fluid passageway of the yoke to provide venting for the first pressure chamber.
- the internal tube or tubing is fluidly coupled to the first internal fluid passageway of the yoke to provide fluid communication between the first pressure chamber and the atmosphere to provide venting for the first pressure chamber.
- Control fluid is supplied to the second pressure chamber via the second internal fluid passageway of the yoke.
- FIG. 1A a known fluid control valve assembly 100 is shown.
- the fluid control valve assembly 100 includes an actuator 102 coupled to a fluid valve 104 via a yoke 106 .
- FIG. 1B illustrates a cross-sectional view of the actuator 102 and a portion of the yoke 106 of FIG. 1A .
- the actuator 102 includes a diaphragm plate 108 and a diaphragm 110 disposed in an actuator casing 112 to define a first (e.g., upper in the orientation shown) pressure chamber 114 and second (e.g., lower in the orientation shown) pressure chamber 116 .
- a controller (e.g., positioner) 118 FIG. 1A ) provides a control fluid (e.g., air) to the first and/or second pressure chambers 114 and/or 116 via external tubing 120 and/or 122 .
- a control fluid e.g., air
- the external tubing 120 and/or 122 poses challenges for manufacturing and reliability.
- tubing When tubing is purchased in bulk, it typically comes in straight lengths. To prepare the tubing for assembly with a valve actuator, the tubing must be cut and bent to shape. In addition, the ends of the tubing must be flared and fittings attached thereto. Specialized tools and fixtures are often required for these processes.
- material selection of external tubing and fittings is often dictated by their intended operative environment. For example, certain operative environments (e.g., highly corrosive environments) may require the external tubing and fittings to be made of particular expensive materials, such as stainless steel, copper or MonelTM, for example.
- fluid and/or media flowing through a valve body of a fluid valve can impart torsional forces on valve components, thereby causing a flow control member and/or a valve stem to twist or turn relative to the valve body.
- Such twisting or turning can damage valve components such as seals.
- such twisting or turning can cause measurement inaccuracies for certain types of valve controllers, such as those that utilize non-contact travel feedback.
- the anti-rotation yoke assembly 200 couples an actuator (not shown) to a valve body (not shown).
- An actuator stem 202 extends through a central axis 204 of the yoke assembly 200 .
- the yoke assembly 200 includes a first end 206 and a second end (not shown) opposite the first end 206 .
- a first arm 208 and a second arm 210 spaced from the first arm 208 extend from the first end 206 to the second end to define an open inner portion 212 .
- a guide rail 214 extends from an inner face 216 of the first arm 208 into the open inner portion 212 .
- a stem connector 218 is fixably coupled to the actuator stem 202 and includes a channel 220 slidably coupled to the guide rail 214 .
- the guide rail 214 and the channel 220 allow the stem connector 218 , and therefore the actuator stem 202 , to slide along the central axis 204 of the yoke assembly 200 , while preventing the actuator stem 202 from rotating with respect to the central axis 204 of the yoke assembly 200 .
- the anti-rotation yoke assembly 200 is typically exposed to the external environment. Therefore, various types of debris can become lodged between the guide rail 214 and the channel 220 of the stem connector 218 , thereby causing increased friction or binding therebetween. Furthermore, other objects can be pinched between the guide rail 214 and the channel 220 of the stem connector 218 . Thus, for at least these reasons, it is desirable for anti-rotation features to be within an enclosure rather than exposed to the external environment.
- the example actuator apparatus 300 includes a yoke 302 to couple an actuator 304 to a fluid valve (e.g., the fluid valve 104 of FIG. 1A ).
- the actuator 304 includes an actuator casing 306 and a load apparatus comprising a diaphragm plate 308 and a diaphragm 310 positioned in the actuator casing 306 to define a first (e.g., upper) pressure chamber 312 and a second (e.g., lower) pressure chamber 314 opposite the first pressure chamber 312 .
- the diaphragm plate 308 defines a spring seating surface 316 for one or more springs 318 .
- An actuator stem 320 is fixably coupled to the diaphragm plate 308 such that movement of the diaphragm 310 and the diaphragm plate 308 causes movement of the actuator stem 320 and, therefore, of a valve stem (not shown) fixably coupled to the actuator stem 320 .
- the example actuator apparatus 300 is a direct-acting (e.g., air-to-close) actuator.
- control fluid is supplied to the first pressure chamber 312 and the second pressure chamber 314 vents to the atmosphere. Applying control fluid to the first pressure chamber 312 extends the actuator stem 320 out of the actuator casing 306 .
- the opposing spring force from the spring 318 retracts the actuator stem 320 into the actuator casing 306 .
- the spring 318 forces the actuator stem 320 and, therefore, the valve stem (not shown) and flow control member (not shown) attached thereto to the extreme retracted (e.g., upwards in the orientation shown) position. This action may be used to provide fail-to-open operation.
- the yoke 302 includes a first arm 322 having a first internal fluid passageway 324 , and a second arm 326 having a second internal fluid passageway 328 .
- the first internal fluid passageway 324 is in fluid communication with the second pressure chamber 314 and with the atmosphere via a vent (not shown), thereby providing venting for the second pressure chamber 314 .
- a tube 330 is fluidly coupled to the second internal fluid passageway 328 and extends through an opening 332 in the diaphragm plate 308 .
- a controller e.g., the controller 118 of FIG. 1A
- the tube 330 is fluidly coupled to the second internal fluid passageway 328 .
- a controller (not shown) is fluidly coupled to the second internal fluid passageway 328 to provide control fluid to the first pressure chamber 312 via the tube 330 .
- the tube 330 is coupled to the second internal fluid passageway 328 via (1) pipe threads (via, e.g., NPT pipe threads) on the tube 330 and in the second internal fluid passageway 328 ; (2) welding the tube 330 to the second internal fluid passageway 328 ; (3) connectors; or (4) any other suitable coupling techniques. As shown in FIG.
- the tube 330 extends through the opening 332 in the diaphragm plate 308 to provide fluid communication between the first pressure chamber 312 and the second internal fluid passageway 328 . Since the tube 330 is completely internal to the actuator apparatus 300 , the tube 330 is not exposed to the harsh environmental conditions to which external tubing is often exposed. Accordingly, the tube 330 need not be constructed of expensive, anti-corrosive materials. In certain examples, the tube 330 is constructed of steel (e.g., galvanized or stainless steel), copper, polymers (e.g., PVC or ABS), or other materials. Moreover, a single size tube can be used in each of the configurations.
- the opening 332 in the diaphragm plate 308 includes a bushing 334 and a seal 336 , each of which is coaxial to the opening 332 and the tube 330 .
- the bushing 334 has an inside diameter that is slightly larger than an outside diameter of the tube 330 .
- the bushing 334 facilitates axial movement (e.g., sliding) of the diaphragm plate 308 relative to the tube 330 .
- the tube 330 also acts to maintain the alignment of such axial movement during operation. Therefore, the tube 330 provides an anti-rotation mechanism by preventing the diaphragm plate 308 from rotating relative to the actuator casing 306 .
- the bushing 334 comprises a polymer (e.g., nylon) and/or other types of low friction and/or self-lubricating materials.
- the bushing 334 is eliminated by constructing the diaphragm plate 308 and/or the tube 330 of certain materials, such as Nitronic 60 , which exhibits resistance to wear and galling.
- the seal 336 is disposed within the opening 332 near the first pressure chamber 312 (e.g., adjacent a pressurized side of the diaphragm plate 308 ).
- the seal prevents control fluid from leaking from the first pressure chamber 312 into the second pressure chamber 314 via the opening 332 .
- the seal 336 is an o-ring or gasket.
- FIGS. 4A and 4B another example actuator apparatus 400 with internal tubing and an anti-rotation mechanism is illustrated in accordance with the present disclosure.
- the example actuator apparatus 400 is a reverse-acting (e.g., air-to-open) actuator, as opposed to the direct-acting actuator apparatus 300 of FIG. 3 .
- the actuator apparatus 400 of FIG. 4A utilizes many of the same components as the actuator apparatus 300 of FIG. 3A .
- the actuator apparatus 400 of FIG. 4A utilizes the same components as the actuator apparatus 300 of FIG. 3A .
- the actuator apparatus 400 is configurable or field reversible such that rearranging the components of the reverse-acting actuator apparatus 400 produces the direct-acting actuator apparatus 300 of FIG. 3A without requiring additional parts.
- the actuator apparatus 400 provides additional functionality to users compared to known actuators that are not field-reversible.
- Manufacturing operations incur cost for each unique component part. Reducing the number of unique components by combining multiple configurations into a single Stock Keeping Unit (SKU) reduces inventory carrying costs and simplifies inventory management processes. Eliminating redundant parts reduces inventory complexity and simplifies part number management and BOM (Bill of Materials) tracking. A reduction in the number of unique physical items reduces storage space requirements and eliminates manufacturing errors due to common build processes. A smaller subset of components to manage reduces support costs and allows for additional focus on just-in-time or other enhanced inventory planning methodologies.
- SKU Stock Keeping Unit
- Simplifying unique direct-acting and reverse-acting actuators into a single SKU reduces fixed support costs and improves operating efficiency.
- a single configuration directly reduces the spare part inventory required and decreases the opportunity for extended downtime due to out-of-inventory spare parts.
- the use of a single SKU streamlines training required by repair technicians and reduces the opportunity for repair defects due to standard repair processes and spare part kits.
- a successful repair on the first attempt minimizes downtime and can increase safety by eliminating repetitive trips to parts of a process plant.
- the example actuator apparatus 400 of FIG. 4 includes many, if not all of the same components of the actuator apparatus 300 of FIG. 3A .
- the example actuator apparatus 400 includes a yoke 402 to couple an actuator 404 to a fluid valve (e.g., the fluid valve 104 of FIG. 1A ).
- the actuator 404 includes an actuator casing 406 and a load apparatus comprising a diaphragm plate 408 and a diaphragm 410 positioned in the actuator casing 406 to define a first (e.g., upper) pressure chamber 412 and a second (e.g., lower) pressure chamber 414 opposite the first pressure chamber 412 .
- the diaphragm plate 408 defines a spring seating surface for one or more springs 416 .
- An actuator stem 418 is fixably coupled to the diaphragm plate 408 such that movement of the diaphragm 410 and the diaphragm plate 408 causes movement of the actuator stem 418 and, therefore, of a valve stem (not shown) fixably coupled to the actuator stem 418 .
- the example actuator apparatus 400 is a reverse-acting (e.g., air-to-open) actuator.
- control fluid is supplied to the second pressure chamber 414 and the first pressure chamber 412 vents to the atmosphere. Applying control fluid to the second pressure chamber 414 retracts the actuator stem 418 into the actuator casing 406 .
- the opposing spring force from the spring 416 extends the actuator stem 418 out of the actuator casing 406 . Should the control fluid pressure fail, the spring 416 forces the actuator stem 418 and, therefore, the valve stem (not shown) and flow control member (not shown) attached thereto to the extreme downward position. This provides fail-to-close operation.
- the yoke 402 includes a first end 420 and a second end (not shown) opposite the first end 420 .
- a first arm 422 and a second arm 424 spaced from the first arm 422 extend from the first end 420 to the second end to define an open inner portion 426 .
- a first internal fluid passageway 428 is disposed in the first arm 422 and a second internal fluid passageway 430 is disposed in the second arm 424 .
- a tube 432 is fluidly coupled to the first internal fluid passageway 428 , which is in fluid communication with the atmosphere via a vent (not shown).
- the tube 432 extends through an opening 434 in the diaphragm plate 408 to provide fluid communication between the first pressure chamber 412 and the atmosphere.
- a controller e.g., the controller 118 of FIG. 1A
- the tube 432 extends through the opening 434 in the diaphragm plate 408 to provide fluid communication between the first pressure chamber 412 and the atmosphere.
- the opening 434 in the diaphragm plate 408 includes a bushing 436 and a seal 438 , each of which is coaxial to the opening 434 and the tube 432 .
- the bushing 436 and the seal 438 are similar to or the same as the bushing 334 and the seal 336 of FIG. 3B .
- the seal 438 is disposed within the opening 434 near the first pressure chamber 412 (e.g., adjacent a pressurized side 440 of the diaphragm plate 408 ).
- the seal 438 prevents control fluid from leaking from the first pressure chamber 412 into the second pressure chamber 414 via the opening 434 .
- the tube 432 also facilitates venting of the first pressure chamber 412 to the atmosphere via the first internal fluid passageway 428 of the yoke 402 .
- the example actuator apparatus 400 does not require venting through an upper section of the actuator casing 406 . Such vents are directly exposed to harsh environmental conditions (e.g., rain) and, thus, are prone to leaking.
- harsh environmental conditions e.g., rain
- vents By venting through the first internal fluid passageway 428 of the yoke 402 , which is less exposed to external environmental conditions, less robust and/or less expensive vents may be utilized. In other examples, vents can be eliminated.
- the example actuator apparatus 400 provides improved reliability at a reduced cost compared to known actuators.
- the diaphragm 410 of FIGS. 4A and 4B is circular in shape and has a central aperture.
- An inner portion 442 of the diaphragm 410 includes a hook-shaped feature or lip 444 that is captured between the diaphragm plate 408 and a complimentary hook-shaped feature or lip 446 of a retainer ring 448 of the diaphragm plate 408 .
- the diaphragm 410 of FIGS. 4A and 4B is similar to the diaphragm 310 of FIGS. 3A and 3B .
- the example actuator apparatus 500 is a direct-acting (e.g., air-to-close) actuator.
- the example actuator apparatus 500 includes a diaphragm 502 that extends across a pressurized face 504 of a diaphragm plate 506 .
- the diaphragm 502 and the diaphragm plate 506 include openings 508 and 510 to accommodate a tube 512 and an actuator shaft 514 , respectively.
- a flanged bushing 516 retains the diaphragm 502 against the pressurized face 504 of the diaphragm plate 506 .
- a unitary diaphragm plate 506 is implemented, as opposed to the two-piece diaphragm plate 408 including the retainer ring 448 that is employed in the actuator apparatus 300 and 400 of FIGS. 3A-4B .
- the flanged bushing 516 is coaxial to the tube 512 and the opening 508 in the diaphragm 502 and the diaphragm plate 506 .
- the flanged bushing 516 includes a flange portion 518 to retain the diaphragm 502 against the diaphragm plate 506 , and a sleeve portion 520 to facilitate axial movement (e.g., sliding) of the diaphragm plate 506 relative to the tube 512 .
- the flanged bushing 516 includes a seal 522 (e.g., an o-ring or gasket) to prevent control fluid from leaking along the tube 512 .
- a retainer or fastener 524 is threadably coupled to the flanged bushing 516 on a side of the diaphragm plate 506 opposite the diaphragm 502 .
- the retainer 524 is a nut. Tightening the retainer 524 compresses the diaphragm 502 between the diaphragm plate 506 and the flange portion 518 of the flanged bushing 516 , thereby retaining the diaphragm 502 against the diaphragm plate 506 .
- the example actuator apparatus 600 is a reverse-acting (e.g., air-to-open) actuator, whereas the example actuator apparatus 500 of FIGS. 5A and 5B is a direct-acting (e.g., air-to-close) actuator.
- the example actuator apparatus 600 includes a diaphragm 602 that extends across a pressurized face 604 of a diaphragm plate 606 .
- the diaphragm 602 includes openings 608 and 610 to accommodate a tube 612 and an actuator shaft 614 , respectively.
- a flanged bushing 616 retains the diaphragm 602 against the pressurized face 604 of the diaphragm plate 606 .
- the example actuator apparatus 700 , 800 , 900 , 1000 , 1100 and 1200 may include internal fluid passageways (e.g., the internal fluid passageways 324 , 328 , 428 , 430 of FIGS. 3A-4B ) and a tube or tubing (e.g., the tube 330 , 432 , 512 , 612 of FIGS. 3A-6B ).
- the example actuator apparatus 700 , 800 and 900 are direct-acting (e.g., air-to-close) actuators, whereas the example actuator apparatus 1000 , 1100 and 1200 are reverse-acting (e.g., air-to-open) actuators.
- Bench set refers to an initial compression placed on an actuator spring with a spring adjuster. For air-to-open valves, a lower bench set determines the amount of seat load force available and the pressure required to begin valve-opening travel. For air-to-close valves, the lower bench set determines the pressure required to begin valve-closing travel.
- the example actuator apparatus 700 of FIG. 7 is a direct-acting actuator with a non-adjustable bench set.
- the example actuator apparatus 800 of FIG. 8 is a direct-acting actuator with an adjustable bench set.
- the example actuator apparatus 800 includes a spring adjuster 802 threadably coupled to an actuator casing 804 .
- the spring adjuster 802 further includes a spring seat 806 , which abuts the one or more springs 808 .
- Bench set is adjusted by rotating the spring adjuster 802 relative to the actuator casing 804 , which changes the compression of the spring 808 .
- the example actuator apparatus 900 of FIG. 9 is a direct-acting actuator with an adjustable bench set and a double diaphragm.
- the example actuator apparatus 900 includes a spring adjuster 902 threadably coupled to an actuator casing 904 .
- the spring adjuster 902 further includes a spring seat 906 , which abuts the one or more springs 908 .
- Bench set is adjusted by rotating the spring adjuster 902 relative to the actuator casing 904 , which changes the compression of the spring 908 .
- the example actuator apparatus 900 further includes first and second diaphragms 910 , 912 . Double diaphragm actuators, such as the example actuator apparatus 900 , provide improved control precision, decreased operational friction, and increased diaphragm force, as compared to single diaphragm actuators.
- the example actuator apparatus 1000 of FIG. 10 is a reverse-acting actuator with a non-adjustable bench set.
- the example actuator apparatus 1100 of FIG. 11 is a reverse-acting actuator with an adjustable bench set.
- the example actuator apparatus 1100 includes a spring adjuster 1102 threadably coupled to an actuator casing 1104 .
- the spring adjuster 1102 is further coupled to a spring seat 1106 , which abuts the one or more springs 1108 .
- Bench set is adjusted by rotating the spring adjuster 1102 relative to the actuator casing 1104 , which changes the compression of the spring 1108 .
- the example actuator apparatus 1200 of FIG. 12 is a reverse-acting actuator with an adjustable bench set and a double diaphragm.
- the example actuator apparatus 1200 includes a spring adjuster 1202 threadably coupled to an actuator casing 1204 .
- the spring adjuster 1202 is further coupled to a spring seat 1206 , which abuts the one or more springs 1208 .
- Bench set is adjusted by rotating the spring adjuster 1202 relative to the actuator casing 1204 , which changes the compression of the spring(s) 1208 .
- the example actuator apparatus 1200 further includes first and second diaphragms 1210 , 1212 . Double diaphragm actuators, such as the example actuator apparatus 1200 , provide improved control precision, decreased operational friction, and increased diaphragm force, as compared to single diaphragm actuators.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Actuator (AREA)
- Fluid-Driven Valves (AREA)
Abstract
Description
- This patent relates generally to actuators and, more particularly, to actuator apparatus having internal tubing and anti-rotation features.
- Fluid control valves are commonly used in process control systems to control the flow of process fluids. A fluid control valve assembly typically includes an actuator operatively coupled to a flow control member (e.g., a valve gate, a plug, a closure member, etc.) of a fluid valve. The actuator controls the position of the flow control member with respect to a valve seat to control or regulate fluid flow through the valve.
- In operation, a controller (e.g., a positioner) is often employed to supply a control fluid (e.g., air) to a chamber of the actuator to cause movement of a load apparatus (e.g., a diaphragm) which, in turn, controls the position of the flow control member. In some examples, a yoke is employed to couple the actuator to the fluid valve. Additionally, in some instances, the controller is mounted to the yoke.
- Known fluid control valves often employ external tubing to fluidly couple a control fluid between the controller and a chamber (e.g., a pressure chamber) of the actuator. However, the external tubing may become damaged or dislodged, thereby affecting the accuracy of the actuator and, thus, a desired fluid flow through the valve.
- In addition, fluid flowing through a valve body can impart torsional loads on the flow control member, which can be transmitted to the actuator. These torsional loads can damage valve seating surfaces and/or internal actuator components, thereby affecting the accuracy of the actuator and, thus, a desired fluid flow through the valve.
- An example apparatus includes an actuator casing and a diaphragm plate disposed within the actuator casing. The diaphragm plate defines a first pressure chamber and a second pressure chamber opposite the first pressure chamber. A yoke couples the actuator casing to a fluid valve. The yoke includes a first internal fluid passageway in fluid communication with atmosphere and a second internal fluid passageway to receive a control fluid from a controller. A tube fluidly couples the first or second internal fluid passageway to the first pressure chamber via an opening in the diaphragm plate. The tube also prevents the diaphragm plate from rotating relative to the actuator casing.
- Another example apparatus includes a diaphragm plate disposed within an actuator casing and defining first and second pressure chambers. A yoke is coupled to the actuator casing and has first and second fluid passageways. A tube fluidly couples the first pressure chamber to one of the first and second fluid passageways in the yoke. The tube extends through an opening in the diaphragm plate to prevent the diaphragm plate from rotating relative to the actuator casing.
- Another example apparatus includes means for actuating a fluid valve and means for attaching the means for actuating to the fluid valve. The example apparatus also includes first means for fluidly coupling a first pressure chamber of the means for actuating to atmosphere. A portion of the first means for fluidly coupling is integrally formed with the means for attaching. In addition, the example apparatus includes second means for fluidly coupling a second pressure chamber of the means for actuating to a control fluid without the use of external tubing. A portion of the second means for fluidly coupling is integrally formed with the means for attaching. In addition, the first or second means for fluidly coupling further includes means for preventing a valve stem of the fluid valve from rotating relative to the fluid valve.
-
FIG. 1A illustrates a known fluid control valve assembly having external tubing. -
FIG. 1B illustrates a partial cross-sectional view of an actuator and yoke of the known fluid control valve ofFIG. 1A . -
FIG. 2 illustrates a known actuator apparatus with an anti-rotation feature. -
FIG. 3A illustrates an example direct-acting actuator apparatus with internal tubing and an anti-rotation mechanism. -
FIG. 3B illustrates a detail view of the example direct-acting actuator apparatus ofFIG. 3A . -
FIG. 4A illustrates an example reverse-acting actuator apparatus with internal tubing and an anti-rotation mechanism. -
FIG. 4B illustrates a detail view of the example reverse-acting actuator apparatus ofFIG. 4A . -
FIG. 5A illustrates an example direct-acting actuator apparatus with internal tubing, an anti-rotation mechanism and a unitary diaphragm plate. -
FIG. 5B illustrates a detail view of the example direct-acting actuator apparatus ofFIG. 5A . -
FIG. 6A illustrates an example reverse-acting actuator apparatus with internal tubing, an anti-rotation mechanism and a unitary diaphragm plate. -
FIG. 6B illustrates a detail view of the example reverse-acting actuator apparatus ofFIG. 6A . -
FIG. 7 illustrates an example direct-acting actuator apparatus having a non-adjustable bench set. -
FIG. 8 illustrates an example direct-acting actuator apparatus having an adjustable bench set. -
FIG. 9 illustrates an example direct-acting actuator apparatus having an adjustable bench set and a double diaphragm. -
FIG. 10 illustrates an example reverse-acting actuator apparatus having a non-adjustable bench set. -
FIG. 11 illustrates an example reverse-acting actuator apparatus having an adjustable bench set. -
FIG. 12 illustrates an example reverse-acting actuator apparatus having an adjustable bench set and a double diaphragm. - Example actuator apparatus disclosed herein eliminate the need for external tubing to fluidly couple a control fluid supply (via, e.g., a controller or a positioner) to a chamber (e.g., a pressure chamber) of a fluid valve actuator for both direct-acting and reverse-acting actuator configurations. In addition, example actuator apparatus disclosed herein include an anti-rotation apparatus to prevent a valve stem from rotating with respect to a valve. Moreover, example apparatus disclosed herein provide venting through a yoke coupled to the actuator.
- Valve actuators are typically available in direct-acting and reverse-acting configurations. In direct-acting configurations, increasing the pressure of a control fluid (e.g., air) supplied to the actuator pushes the diaphragm down, thereby extending the actuator stem. In reverse-acting configurations, increasing the pressure of a control fluid supplied to the actuator pushes the diaphragm up, thereby retracting the actuator stem. Direct-acting actuators are often referred to as air-to-close actuators because increasing air pressure to the actuator extends the actuator stem, which causes the flow control member to move towards the valve seat, thereby restricting fluid flow. However, certain actuators are configured such that extending the actuator stem causes the flow control member to move away from the valve seat, thereby enabling fluid flow. Similarly, reverse-acting actuators are often referred to as air-to-open actuators because increasing air pressure to the actuator retracts the actuator stem, which causes the flow control member to move away from the valve seat, thereby enabling fluid flow. However, certain actuators are configured such that retracting the actuator stem causes the flow control member to move towards the valve seat, thereby restricting fluid flow. For the purposes of this disclosure, example actuator apparatus are described in which direct-acting actuators are air-to-close actuators and reverse-acting actuators are air-to-open actuators. However, the present disclosure is also applicable to actuators in which direct-acting actuators are air-to-open actuators and reverse-acting actuators are air-to-close actuators. Furthermore, the control fluid employed by actuators in accordance with the present disclosure need not be air. Also, for the purposes of this disclosure, example actuator apparatus are described as diaphragm actuators. However, the present disclosure is also applicable to other types of actuator apparatus, such as piston actuators.
- Example actuator apparatus disclosed herein include a yoke with internal fluid passageways. Specifically, an internal tube or tubing may fluidly couple a first pressure chamber of the actuator with one of first and second internal fluid passageways of the yoke via an opening in a diaphragm plate. In an example, the internal tubing is rigid and also prevents the diaphragm from rotating, thereby preventing the valve trim from rotating due to torsional forces imparted by fluid flowing through the valve body.
- In a direct-acting (e.g., air-to-close) configuration, the internal tube or tubing is fluidly coupled to the second internal fluid passageway of the yoke to supply control fluid to the first pressure chamber. The second pressure chamber is in fluid communication with atmosphere via the first internal fluid passageway of the yoke to provide venting for the first pressure chamber.
- In a reverse-acting (e.g., air-to-open) configuration, the internal tube or tubing is fluidly coupled to the first internal fluid passageway of the yoke to provide fluid communication between the first pressure chamber and the atmosphere to provide venting for the first pressure chamber. Control fluid is supplied to the second pressure chamber via the second internal fluid passageway of the yoke.
- Before describing the example actuator apparatus as mentioned above, a brief description of a known fluid control valve assembly is provided in connection with
FIGS. 1A and 1B . Referring toFIG. 1A , a known fluidcontrol valve assembly 100 is shown. The fluidcontrol valve assembly 100 includes anactuator 102 coupled to afluid valve 104 via ayoke 106. -
FIG. 1B illustrates a cross-sectional view of theactuator 102 and a portion of theyoke 106 ofFIG. 1A . Theactuator 102 includes adiaphragm plate 108 and adiaphragm 110 disposed in anactuator casing 112 to define a first (e.g., upper in the orientation shown)pressure chamber 114 and second (e.g., lower in the orientation shown)pressure chamber 116. A controller (e.g., positioner) 118 (FIG. 1A ) provides a control fluid (e.g., air) to the first and/orsecond pressure chambers 114 and/or 116 viaexternal tubing 120 and/or 122. - The
external tubing 120 and/or 122, however, poses challenges for manufacturing and reliability. When tubing is purchased in bulk, it typically comes in straight lengths. To prepare the tubing for assembly with a valve actuator, the tubing must be cut and bent to shape. In addition, the ends of the tubing must be flared and fittings attached thereto. Specialized tools and fixtures are often required for these processes. Furthermore, material selection of external tubing and fittings is often dictated by their intended operative environment. For example, certain operative environments (e.g., highly corrosive environments) may require the external tubing and fittings to be made of particular expensive materials, such as stainless steel, copper or Monel™, for example. - Turning now to
FIG. 2 , a knownanti-rotation yoke assembly 200 is illustrated. In certain examples, fluid and/or media flowing through a valve body of a fluid valve can impart torsional forces on valve components, thereby causing a flow control member and/or a valve stem to twist or turn relative to the valve body. Such twisting or turning can damage valve components such as seals. In addition, such twisting or turning can cause measurement inaccuracies for certain types of valve controllers, such as those that utilize non-contact travel feedback. - The
anti-rotation yoke assembly 200 couples an actuator (not shown) to a valve body (not shown). An actuator stem 202 extends through acentral axis 204 of theyoke assembly 200. Theyoke assembly 200 includes afirst end 206 and a second end (not shown) opposite thefirst end 206. Afirst arm 208 and asecond arm 210 spaced from thefirst arm 208 extend from thefirst end 206 to the second end to define an openinner portion 212. Aguide rail 214 extends from aninner face 216 of thefirst arm 208 into the openinner portion 212. Astem connector 218 is fixably coupled to theactuator stem 202 and includes achannel 220 slidably coupled to theguide rail 214. More specifically, theguide rail 214 and thechannel 220 allow thestem connector 218, and therefore theactuator stem 202, to slide along thecentral axis 204 of theyoke assembly 200, while preventing the actuator stem 202 from rotating with respect to thecentral axis 204 of theyoke assembly 200. - The
anti-rotation yoke assembly 200 is typically exposed to the external environment. Therefore, various types of debris can become lodged between theguide rail 214 and thechannel 220 of thestem connector 218, thereby causing increased friction or binding therebetween. Furthermore, other objects can be pinched between theguide rail 214 and thechannel 220 of thestem connector 218. Thus, for at least these reasons, it is desirable for anti-rotation features to be within an enclosure rather than exposed to the external environment. - Turning now to
FIGS. 3A and 3B , anexample actuator apparatus 300 with internal tubing and an anti-rotation mechanism is illustrated in accordance with the present disclosure. Turning toFIG. 3A , theexample actuator apparatus 300 includes ayoke 302 to couple anactuator 304 to a fluid valve (e.g., thefluid valve 104 ofFIG. 1A ). Theactuator 304 includes anactuator casing 306 and a load apparatus comprising adiaphragm plate 308 and adiaphragm 310 positioned in theactuator casing 306 to define a first (e.g., upper)pressure chamber 312 and a second (e.g., lower) pressure chamber 314 opposite thefirst pressure chamber 312. Thediaphragm plate 308 defines aspring seating surface 316 for one or more springs 318. An actuator stem 320 is fixably coupled to thediaphragm plate 308 such that movement of thediaphragm 310 and thediaphragm plate 308 causes movement of theactuator stem 320 and, therefore, of a valve stem (not shown) fixably coupled to theactuator stem 320. - The
example actuator apparatus 300 is a direct-acting (e.g., air-to-close) actuator. For direct-acting actuators, control fluid is supplied to thefirst pressure chamber 312 and the second pressure chamber 314 vents to the atmosphere. Applying control fluid to thefirst pressure chamber 312 extends theactuator stem 320 out of theactuator casing 306. When the pressure of the control fluid is reduced, the opposing spring force from thespring 318 retracts theactuator stem 320 into theactuator casing 306. Should the control fluid pressure fail, thespring 318 forces theactuator stem 320 and, therefore, the valve stem (not shown) and flow control member (not shown) attached thereto to the extreme retracted (e.g., upwards in the orientation shown) position. This action may be used to provide fail-to-open operation. - The
yoke 302 includes afirst arm 322 having a firstinternal fluid passageway 324, and asecond arm 326 having a secondinternal fluid passageway 328. The firstinternal fluid passageway 324 is in fluid communication with the second pressure chamber 314 and with the atmosphere via a vent (not shown), thereby providing venting for the second pressure chamber 314. Atube 330 is fluidly coupled to the secondinternal fluid passageway 328 and extends through anopening 332 in thediaphragm plate 308. A controller (e.g., thecontroller 118 ofFIG. 1A ) is fluidly coupled to the secondinternal fluid passageway 328, which is in fluid communication with thefirst pressure chamber 312 via thetube 330, to provide control fluid to thefirst pressure chamber 312. - As shown in
FIG. 3B , thetube 330 is fluidly coupled to the secondinternal fluid passageway 328. A controller (not shown) is fluidly coupled to the secondinternal fluid passageway 328 to provide control fluid to thefirst pressure chamber 312 via thetube 330. In certain examples, thetube 330 is coupled to the secondinternal fluid passageway 328 via (1) pipe threads (via, e.g., NPT pipe threads) on thetube 330 and in the secondinternal fluid passageway 328; (2) welding thetube 330 to the secondinternal fluid passageway 328; (3) connectors; or (4) any other suitable coupling techniques. As shown inFIG. 3B , thetube 330 extends through theopening 332 in thediaphragm plate 308 to provide fluid communication between thefirst pressure chamber 312 and the secondinternal fluid passageway 328. Since thetube 330 is completely internal to theactuator apparatus 300, thetube 330 is not exposed to the harsh environmental conditions to which external tubing is often exposed. Accordingly, thetube 330 need not be constructed of expensive, anti-corrosive materials. In certain examples, thetube 330 is constructed of steel (e.g., galvanized or stainless steel), copper, polymers (e.g., PVC or ABS), or other materials. Moreover, a single size tube can be used in each of the configurations. - The
opening 332 in thediaphragm plate 308 includes abushing 334 and aseal 336, each of which is coaxial to theopening 332 and thetube 330. Thebushing 334 has an inside diameter that is slightly larger than an outside diameter of thetube 330. Thebushing 334 facilitates axial movement (e.g., sliding) of thediaphragm plate 308 relative to thetube 330. Thetube 330 also acts to maintain the alignment of such axial movement during operation. Therefore, thetube 330 provides an anti-rotation mechanism by preventing thediaphragm plate 308 from rotating relative to theactuator casing 306. In certain examples, thebushing 334 comprises a polymer (e.g., nylon) and/or other types of low friction and/or self-lubricating materials. In other examples, thebushing 334 is eliminated by constructing thediaphragm plate 308 and/or thetube 330 of certain materials, such as Nitronic 60, which exhibits resistance to wear and galling. - The
seal 336 is disposed within theopening 332 near the first pressure chamber 312 (e.g., adjacent a pressurized side of the diaphragm plate 308). The seal prevents control fluid from leaking from thefirst pressure chamber 312 into the second pressure chamber 314 via theopening 332. In certain examples, theseal 336 is an o-ring or gasket. - Turning now to
FIGS. 4A and 4B , anotherexample actuator apparatus 400 with internal tubing and an anti-rotation mechanism is illustrated in accordance with the present disclosure. Turning toFIG. 4A , theexample actuator apparatus 400 is a reverse-acting (e.g., air-to-open) actuator, as opposed to the direct-actingactuator apparatus 300 ofFIG. 3 . Theactuator apparatus 400 ofFIG. 4A utilizes many of the same components as theactuator apparatus 300 ofFIG. 3A . In certain examples, theactuator apparatus 400 ofFIG. 4A utilizes the same components as theactuator apparatus 300 ofFIG. 3A . Thus, in certain examples, theactuator apparatus 400 is configurable or field reversible such that rearranging the components of the reverse-actingactuator apparatus 400 produces the direct-actingactuator apparatus 300 ofFIG. 3A without requiring additional parts. Thus, theactuator apparatus 400 provides additional functionality to users compared to known actuators that are not field-reversible. - Manufacturing operations incur cost for each unique component part. Reducing the number of unique components by combining multiple configurations into a single Stock Keeping Unit (SKU) reduces inventory carrying costs and simplifies inventory management processes. Eliminating redundant parts reduces inventory complexity and simplifies part number management and BOM (Bill of Materials) tracking. A reduction in the number of unique physical items reduces storage space requirements and eliminates manufacturing errors due to common build processes. A smaller subset of components to manage reduces support costs and allows for additional focus on just-in-time or other enhanced inventory planning methodologies.
- Simplifying unique direct-acting and reverse-acting actuators into a single SKU reduces fixed support costs and improves operating efficiency. A single configuration directly reduces the spare part inventory required and decreases the opportunity for extended downtime due to out-of-inventory spare parts. In addition, the use of a single SKU streamlines training required by repair technicians and reduces the opportunity for repair defects due to standard repair processes and spare part kits. A successful repair on the first attempt minimizes downtime and can increase safety by eliminating repetitive trips to parts of a process plant.
- The
example actuator apparatus 400 ofFIG. 4 includes many, if not all of the same components of theactuator apparatus 300 ofFIG. 3A . Theexample actuator apparatus 400 includes ayoke 402 to couple anactuator 404 to a fluid valve (e.g., thefluid valve 104 ofFIG. 1A ). Theactuator 404 includes anactuator casing 406 and a load apparatus comprising adiaphragm plate 408 and adiaphragm 410 positioned in theactuator casing 406 to define a first (e.g., upper) pressure chamber 412 and a second (e.g., lower)pressure chamber 414 opposite the first pressure chamber 412. Thediaphragm plate 408 defines a spring seating surface for one or more springs 416. An actuator stem 418 is fixably coupled to thediaphragm plate 408 such that movement of thediaphragm 410 and thediaphragm plate 408 causes movement of theactuator stem 418 and, therefore, of a valve stem (not shown) fixably coupled to theactuator stem 418. - As mentioned above, the
example actuator apparatus 400 is a reverse-acting (e.g., air-to-open) actuator. For reverse-acting actuators, control fluid is supplied to thesecond pressure chamber 414 and the first pressure chamber 412 vents to the atmosphere. Applying control fluid to thesecond pressure chamber 414 retracts theactuator stem 418 into theactuator casing 406. When the pressure of the control fluid is reduced, the opposing spring force from thespring 416 extends theactuator stem 418 out of theactuator casing 406. Should the control fluid pressure fail, thespring 416 forces theactuator stem 418 and, therefore, the valve stem (not shown) and flow control member (not shown) attached thereto to the extreme downward position. This provides fail-to-close operation. - The
yoke 402 includes afirst end 420 and a second end (not shown) opposite thefirst end 420. Afirst arm 422 and asecond arm 424 spaced from thefirst arm 422 extend from thefirst end 420 to the second end to define an openinner portion 426. A firstinternal fluid passageway 428 is disposed in thefirst arm 422 and a secondinternal fluid passageway 430 is disposed in thesecond arm 424. Atube 432 is fluidly coupled to the firstinternal fluid passageway 428, which is in fluid communication with the atmosphere via a vent (not shown). Thetube 432 extends through anopening 434 in thediaphragm plate 408 to provide fluid communication between the first pressure chamber 412 and the atmosphere. A controller (e.g., thecontroller 118 ofFIG. 1A ) is fluidly coupled to the secondinternal fluid passageway 430, which is in fluid communication with thesecond pressure chamber 414, to provide control fluid to thesecond pressure chamber 414. - As shown in
FIG. 4B , thetube 432 extends through theopening 434 in thediaphragm plate 408 to provide fluid communication between the first pressure chamber 412 and the atmosphere. Theopening 434 in thediaphragm plate 408 includes abushing 436 and aseal 438, each of which is coaxial to theopening 434 and thetube 432. Thebushing 436 and theseal 438 are similar to or the same as thebushing 334 and theseal 336 ofFIG. 3B . Theseal 438 is disposed within theopening 434 near the first pressure chamber 412 (e.g., adjacent apressurized side 440 of the diaphragm plate 408). Theseal 438 prevents control fluid from leaking from the first pressure chamber 412 into thesecond pressure chamber 414 via theopening 434. - The
tube 432 also facilitates venting of the first pressure chamber 412 to the atmosphere via the firstinternal fluid passageway 428 of theyoke 402. Thus, theexample actuator apparatus 400 does not require venting through an upper section of theactuator casing 406. Such vents are directly exposed to harsh environmental conditions (e.g., rain) and, thus, are prone to leaking. By venting through the firstinternal fluid passageway 428 of theyoke 402, which is less exposed to external environmental conditions, less robust and/or less expensive vents may be utilized. In other examples, vents can be eliminated. Thus, theexample actuator apparatus 400 provides improved reliability at a reduced cost compared to known actuators. - The
diaphragm 410 ofFIGS. 4A and 4B is circular in shape and has a central aperture. Aninner portion 442 of thediaphragm 410 includes a hook-shaped feature orlip 444 that is captured between thediaphragm plate 408 and a complimentary hook-shaped feature orlip 446 of aretainer ring 448 of thediaphragm plate 408. Thediaphragm 410 ofFIGS. 4A and 4B is similar to thediaphragm 310 ofFIGS. 3A and 3B . - Turning now to
FIGS. 5A and 5B , anotherexample actuator apparatus 500 is illustrated. Theexample actuator apparatus 500 is a direct-acting (e.g., air-to-close) actuator. Theexample actuator apparatus 500 includes adiaphragm 502 that extends across apressurized face 504 of adiaphragm plate 506. Thediaphragm 502 and thediaphragm plate 506 includeopenings tube 512 and anactuator shaft 514, respectively. Aflanged bushing 516 retains thediaphragm 502 against thepressurized face 504 of thediaphragm plate 506. In this configuration, aunitary diaphragm plate 506 is implemented, as opposed to the two-piece diaphragm plate 408 including theretainer ring 448 that is employed in theactuator apparatus FIGS. 3A-4B . - Turning now to
FIG. 5B , theflanged bushing 516 is described in further detail. Theflanged bushing 516 is coaxial to thetube 512 and theopening 508 in thediaphragm 502 and thediaphragm plate 506. Theflanged bushing 516 includes aflange portion 518 to retain thediaphragm 502 against thediaphragm plate 506, and asleeve portion 520 to facilitate axial movement (e.g., sliding) of thediaphragm plate 506 relative to thetube 512. In certain examples, theflanged bushing 516 includes a seal 522 (e.g., an o-ring or gasket) to prevent control fluid from leaking along thetube 512. A retainer orfastener 524 is threadably coupled to theflanged bushing 516 on a side of thediaphragm plate 506 opposite thediaphragm 502. In certain examples, theretainer 524 is a nut. Tightening theretainer 524 compresses thediaphragm 502 between thediaphragm plate 506 and theflange portion 518 of theflanged bushing 516, thereby retaining thediaphragm 502 against thediaphragm plate 506. - Turning now to
FIGS. 6A and 6B , anotherexample actuator apparatus 600 is illustrated. Theexample actuator apparatus 600 is a reverse-acting (e.g., air-to-open) actuator, whereas theexample actuator apparatus 500 ofFIGS. 5A and 5B is a direct-acting (e.g., air-to-close) actuator. Similar to theexample actuator apparatus 500 ofFIGS. 5A and 5B , theexample actuator apparatus 600 includes adiaphragm 602 that extends across apressurized face 604 of adiaphragm plate 606. Thediaphragm 602 includesopenings tube 612 and anactuator shaft 614, respectively. Aflanged bushing 616 retains thediaphragm 602 against thepressurized face 604 of thediaphragm plate 606. - Turning now to
FIGS. 7-12 , further example actuator apparatus with various bench set configurations are illustrated. Theexample actuator apparatus fluid passageways FIGS. 3A-4B ) and a tube or tubing (e.g., thetube FIGS. 3A-6B ). Theexample actuator apparatus example actuator apparatus - The
example actuator apparatus 700 ofFIG. 7 is a direct-acting actuator with a non-adjustable bench set. - The
example actuator apparatus 800 ofFIG. 8 is a direct-acting actuator with an adjustable bench set. Theexample actuator apparatus 800 includes aspring adjuster 802 threadably coupled to anactuator casing 804. Thespring adjuster 802 further includes aspring seat 806, which abuts the one or more springs 808. Bench set is adjusted by rotating thespring adjuster 802 relative to theactuator casing 804, which changes the compression of thespring 808. - The
example actuator apparatus 900 ofFIG. 9 is a direct-acting actuator with an adjustable bench set and a double diaphragm. Theexample actuator apparatus 900 includes aspring adjuster 902 threadably coupled to anactuator casing 904. Thespring adjuster 902 further includes aspring seat 906, which abuts the one or more springs 908. Bench set is adjusted by rotating thespring adjuster 902 relative to theactuator casing 904, which changes the compression of thespring 908. Theexample actuator apparatus 900 further includes first andsecond diaphragms example actuator apparatus 900, provide improved control precision, decreased operational friction, and increased diaphragm force, as compared to single diaphragm actuators. - The
example actuator apparatus 1000 ofFIG. 10 is a reverse-acting actuator with a non-adjustable bench set. - The
example actuator apparatus 1100 ofFIG. 11 is a reverse-acting actuator with an adjustable bench set. Theexample actuator apparatus 1100 includes aspring adjuster 1102 threadably coupled to anactuator casing 1104. Thespring adjuster 1102 is further coupled to aspring seat 1106, which abuts the one ormore springs 1108. Bench set is adjusted by rotating thespring adjuster 1102 relative to theactuator casing 1104, which changes the compression of thespring 1108. - The
example actuator apparatus 1200 ofFIG. 12 is a reverse-acting actuator with an adjustable bench set and a double diaphragm. Theexample actuator apparatus 1200 includes aspring adjuster 1202 threadably coupled to anactuator casing 1204. Thespring adjuster 1202 is further coupled to aspring seat 1206, which abuts the one ormore springs 1208. Bench set is adjusted by rotating thespring adjuster 1202 relative to theactuator casing 1204, which changes the compression of the spring(s) 1208. Theexample actuator apparatus 1200 further includes first andsecond diaphragms example actuator apparatus 1200, provide improved control precision, decreased operational friction, and increased diaphragm force, as compared to single diaphragm actuators. - Although certain example apparatus have been described herein, the scope of coverage of this patent is not limited thereto. On the contrary, this patent covers all methods, apparatus and articles of manufacture fairly falling within the scope of the amended claims either literally or under doctrine of equivalents.
Claims (20)
Priority Applications (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/189,627 US9458947B2 (en) | 2014-02-25 | 2014-02-25 | Actuator apparatus with internal tubing and anti-rotation mechanism |
CN201520227159.7U CN204878988U (en) | 2014-02-25 | 2015-02-16 | Actuator arrangements |
CN201510177945.5A CN104913101B (en) | 2014-02-25 | 2015-02-16 | Actuator devices with internal pipeline and anti-rotation mechanism |
RU2016136694A RU2672235C2 (en) | 2014-02-25 | 2015-02-25 | Actuator apparatus with internal tubing and anti-rotation mechanism |
PCT/US2015/017415 WO2015130726A1 (en) | 2014-02-25 | 2015-02-25 | Actuator apparatus with internal tubing and anti-rotation mechanism |
EP15709021.8A EP3111123B1 (en) | 2014-02-25 | 2015-02-25 | Actuator apparatus with internal tubing and anti-rotation mechanism |
CA2940542A CA2940542C (en) | 2014-02-25 | 2015-02-25 | Actuator apparatus with internal tubing and anti-rotation mechanism |
SA516371739A SA516371739B1 (en) | 2014-02-25 | 2016-08-25 | Actuator Apparatus with Internal Tubing and Anti-Rotation Mechanism |
US15/253,275 US9970567B2 (en) | 2014-02-25 | 2016-08-31 | Actuator apparatus with internal tubing and anti-rotation mechanism |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/189,627 US9458947B2 (en) | 2014-02-25 | 2014-02-25 | Actuator apparatus with internal tubing and anti-rotation mechanism |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/253,275 Continuation US9970567B2 (en) | 2014-02-25 | 2016-08-31 | Actuator apparatus with internal tubing and anti-rotation mechanism |
Publications (2)
Publication Number | Publication Date |
---|---|
US20150240965A1 true US20150240965A1 (en) | 2015-08-27 |
US9458947B2 US9458947B2 (en) | 2016-10-04 |
Family
ID=52633678
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/189,627 Active US9458947B2 (en) | 2014-02-25 | 2014-02-25 | Actuator apparatus with internal tubing and anti-rotation mechanism |
US15/253,275 Active US9970567B2 (en) | 2014-02-25 | 2016-08-31 | Actuator apparatus with internal tubing and anti-rotation mechanism |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/253,275 Active US9970567B2 (en) | 2014-02-25 | 2016-08-31 | Actuator apparatus with internal tubing and anti-rotation mechanism |
Country Status (7)
Country | Link |
---|---|
US (2) | US9458947B2 (en) |
EP (1) | EP3111123B1 (en) |
CN (2) | CN104913101B (en) |
CA (1) | CA2940542C (en) |
RU (1) | RU2672235C2 (en) |
SA (1) | SA516371739B1 (en) |
WO (1) | WO2015130726A1 (en) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150277451A1 (en) * | 2012-10-22 | 2015-10-01 | Emerson Process Management Regulator Technologies, Inc. | Driving Apparatus and Valve Including the Same |
US9291280B2 (en) | 2012-07-12 | 2016-03-22 | Fisher Controls International, Llc | Actuator apparatus having internal passageways |
US20180106384A1 (en) * | 2016-10-17 | 2018-04-19 | Fisher Controls International Llc | Yoke for rotary valve |
US9970567B2 (en) | 2014-02-25 | 2018-05-15 | Fisher Controls International Llc | Actuator apparatus with internal tubing and anti-rotation mechanism |
WO2019036183A1 (en) * | 2017-08-16 | 2019-02-21 | Fisher Control International Llc | Apparatus to bias a moveable tube towards a seal |
EP3450776A1 (en) * | 2017-08-31 | 2019-03-06 | Samson AG | Positioning device for process-technical installations |
US10488872B2 (en) * | 2017-07-07 | 2019-11-26 | Samson Ag | Actuating drive device process valves |
US10701820B1 (en) * | 2019-06-06 | 2020-06-30 | Fisher Controls International Llc | Tamper proof approaches for securing an enclosure |
US20230235834A1 (en) * | 2020-04-16 | 2023-07-27 | Samson Aktiengesellschaft | Actuator for a process plant |
WO2024050284A1 (en) * | 2022-08-31 | 2024-03-07 | Dresser, Llc | Integrating fluid pathways into a valve superstructure |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3874629A (en) * | 1971-11-23 | 1975-04-01 | Fail Safe Brake Corp | Fluid operated needle valve |
US5288052A (en) * | 1992-12-08 | 1994-02-22 | Cashco, Inc. | Self-draining sanitary control valve |
US5699664A (en) * | 1994-11-17 | 1997-12-23 | Sagem Sa | Shut-off valve unit for a circuit for injecting air in the exhaust system of an internal combustion engine |
Family Cites Families (47)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2078553A (en) | 1934-09-22 | 1937-04-27 | C O Two Fire Equipment Co | Discharge head for fluid containers |
US2132199A (en) | 1936-10-12 | 1938-10-04 | Gray Tool Co | Well head installation with choke valve |
CH244911A (en) | 1943-01-25 | 1946-10-15 | Austin Underwood Bryant | Device for controlling the flow of a fluid. |
US2783746A (en) | 1950-06-10 | 1957-03-05 | Grinnell Corp | Double acting fluid pressure actuator |
DE1019878B (en) | 1955-03-25 | 1957-11-21 | Armaturenwerk Eisenberg Veb | Outlet valve without stuffing box |
US2882008A (en) | 1955-07-06 | 1959-04-14 | Louis F Giauque | Pneumatic valve construction |
US3206165A (en) | 1962-08-03 | 1965-09-14 | Hoke Inc | Valve |
NL137883C (en) | 1967-09-11 | |||
DE1926781A1 (en) | 1969-05-24 | 1970-11-26 | Samson Appbau Ag | Membrane drive device for pneumatic membrane valves or the like. |
SU377567A1 (en) * | 1970-06-16 | 1973-04-17 | Институт горной механики , технической кибернетики М. М. Федорова | PNEUMATIC SWITCH |
GB1445588A (en) | 1973-10-23 | 1976-08-11 | English Electric Co Ltd | Fluid-flow control valve |
US3892384A (en) | 1974-04-12 | 1975-07-01 | Honeywell Inc | Double seated cage valve with flexible plug seat |
US4054979A (en) | 1974-07-22 | 1977-10-25 | Robertshaw Controls Company | Valve construction and method of making the same |
US4311297A (en) | 1980-04-04 | 1982-01-19 | Exxon Production Research Company | Pressure insensitive valve |
US4383553A (en) | 1981-10-19 | 1983-05-17 | Exxon Research And Engineering Co. | Visbreaker letdown valve |
US4483512A (en) | 1982-06-25 | 1984-11-20 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Slow opening valve |
EP0134866A2 (en) | 1983-07-18 | 1985-03-27 | Kerotest Manufacturing Corporation | On-off valve |
JPS6051364U (en) | 1983-09-19 | 1985-04-11 | 旭有機材工業株式会社 | gate valve |
US4523436A (en) | 1983-12-22 | 1985-06-18 | Carrier Corporation | Incrementally adjustable electronic expansion valve |
US4671490A (en) | 1986-05-16 | 1987-06-09 | Nupro Co. | Diaphragm valve |
US4763690A (en) | 1986-07-29 | 1988-08-16 | Harsco Corporation | Leak-proof valve for gas cylinders |
DE3703303A1 (en) | 1987-02-04 | 1988-08-18 | Babcock Werke Ag | QUICK-RELEASE GATE VALVE |
DE3727008A1 (en) | 1987-08-13 | 1989-02-23 | Samson Ag | ARRANGEMENT WITH A PNEUMATIC CONTROL VALVE |
US4834133A (en) | 1988-09-28 | 1989-05-30 | Westinghouse Electric Corp. | Control valve |
GB2256028B (en) | 1991-05-20 | 1995-11-01 | Crane Ltd | Fluid-flow valve |
DE9210096U1 (en) * | 1992-07-28 | 1992-09-24 | Arca Regler GmbH, 47918 Tönisvorst | Pneumatic actuator |
DE4244573C2 (en) * | 1992-12-30 | 1995-10-19 | Samson Ag | Pneumatic diaphragm actuator |
DE9300685U1 (en) | 1993-01-20 | 1993-06-09 | Arca Regler GmbH, 4154 Tönisvorst | Pneumatic actuator |
US5704594A (en) | 1995-04-11 | 1998-01-06 | Bw/Ip Internatinal, Inc. | Guided gate valve |
US5706856A (en) | 1995-04-17 | 1998-01-13 | Lancaster; Robert D. | Valve apparatus |
US5722638A (en) | 1995-10-20 | 1998-03-03 | Vemco Corporation | Valve with means to block relative rotation of parts during assembly |
JPH10124150A (en) * | 1996-10-15 | 1998-05-15 | Tlv Co Ltd | Steam pressure reducing valve |
DE19947129A1 (en) | 1999-09-30 | 2001-04-05 | Siemens Ag | Diagnosis system, especially for control |
RU2200265C1 (en) | 2001-06-08 | 2003-03-10 | Малина Петр Васильевич | Valve |
US6536473B2 (en) | 2001-08-02 | 2003-03-25 | Master Flo Valve Inc. | Choke valve |
CN2572166Y (en) * | 2002-09-06 | 2003-09-10 | 徐州阿卡控制阀门有限公司 | Inner air supply regulation type pneuamtic executing mechanism |
US20060049375A1 (en) | 2004-09-07 | 2006-03-09 | Fisher Controls International Llc | Boronized valve seal |
US8256738B2 (en) * | 2007-09-13 | 2012-09-04 | John Leslie Johnson | Double action directional fluid flow valve |
CN201202860Y (en) * | 2008-05-26 | 2009-03-04 | 陈红 | Low pressure regulating valve of gas meter |
US8053941B2 (en) | 2008-12-16 | 2011-11-08 | Nidec Motor Corporation | Encapsulated outer stator isolated rotor stepper motor valve assembly |
JP4627799B2 (en) | 2008-12-19 | 2011-02-09 | シーケーディ株式会社 | Manual valve |
CN201348070Y (en) * | 2009-01-05 | 2009-11-18 | 浙江永盛仪表有限公司 | Actuator for pneumatic diaphragm control valve |
US8152132B2 (en) | 2009-01-30 | 2012-04-10 | Fisher Controls International Llc | Pneumatic actuator having diaphragm retention ring |
DE102009008493A1 (en) | 2009-02-11 | 2010-08-12 | Amazonen-Werke H. Dreyer Gmbh & Co. Kg | Nozzle body for use as motor valve in agricultural sprayer, has sealing element i.e. O-ring, provided between valve plunger and housing, and arranged in area of adjusting element, which is rotary movable for adjusting locking plunger |
US9206909B2 (en) | 2012-01-31 | 2015-12-08 | Fisher Controls International Llc | Anti-rotation assemblies for use with fluid valves |
US9291280B2 (en) | 2012-07-12 | 2016-03-22 | Fisher Controls International, Llc | Actuator apparatus having internal passageways |
US9458947B2 (en) | 2014-02-25 | 2016-10-04 | Fisher Controls International Lc | Actuator apparatus with internal tubing and anti-rotation mechanism |
-
2014
- 2014-02-25 US US14/189,627 patent/US9458947B2/en active Active
-
2015
- 2015-02-16 CN CN201510177945.5A patent/CN104913101B/en active Active
- 2015-02-16 CN CN201520227159.7U patent/CN204878988U/en not_active Withdrawn - After Issue
- 2015-02-25 RU RU2016136694A patent/RU2672235C2/en active
- 2015-02-25 WO PCT/US2015/017415 patent/WO2015130726A1/en active Application Filing
- 2015-02-25 CA CA2940542A patent/CA2940542C/en active Active
- 2015-02-25 EP EP15709021.8A patent/EP3111123B1/en active Active
-
2016
- 2016-08-25 SA SA516371739A patent/SA516371739B1/en unknown
- 2016-08-31 US US15/253,275 patent/US9970567B2/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3874629A (en) * | 1971-11-23 | 1975-04-01 | Fail Safe Brake Corp | Fluid operated needle valve |
US5288052A (en) * | 1992-12-08 | 1994-02-22 | Cashco, Inc. | Self-draining sanitary control valve |
US5699664A (en) * | 1994-11-17 | 1997-12-23 | Sagem Sa | Shut-off valve unit for a circuit for injecting air in the exhaust system of an internal combustion engine |
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9291280B2 (en) | 2012-07-12 | 2016-03-22 | Fisher Controls International, Llc | Actuator apparatus having internal passageways |
US20150277451A1 (en) * | 2012-10-22 | 2015-10-01 | Emerson Process Management Regulator Technologies, Inc. | Driving Apparatus and Valve Including the Same |
US9645587B2 (en) * | 2012-10-22 | 2017-05-09 | Emerson Process Management Regulator Technologies, Inc. | Driving apparatus and valve including the same |
US9970567B2 (en) | 2014-02-25 | 2018-05-15 | Fisher Controls International Llc | Actuator apparatus with internal tubing and anti-rotation mechanism |
US20180106384A1 (en) * | 2016-10-17 | 2018-04-19 | Fisher Controls International Llc | Yoke for rotary valve |
US10539241B2 (en) * | 2016-10-17 | 2020-01-21 | Fisher Controls International Llc | Yoke for rotary valve |
US10488872B2 (en) * | 2017-07-07 | 2019-11-26 | Samson Ag | Actuating drive device process valves |
CN109404597A (en) * | 2017-08-16 | 2019-03-01 | 费希尔控制产品国际有限公司 | For making device of the removable pipeline towards sealing biasing |
WO2019036183A1 (en) * | 2017-08-16 | 2019-02-21 | Fisher Control International Llc | Apparatus to bias a moveable tube towards a seal |
RU2766660C2 (en) * | 2017-08-16 | 2022-03-15 | Фишер Контролз Интернешнел Ллс | Apparatus for displacing a movable tube in the direction of a seal |
EP3450776A1 (en) * | 2017-08-31 | 2019-03-06 | Samson AG | Positioning device for process-technical installations |
US20190072205A1 (en) * | 2017-08-31 | 2019-03-07 | Samson Ag | Control valve for a process plant |
US10701820B1 (en) * | 2019-06-06 | 2020-06-30 | Fisher Controls International Llc | Tamper proof approaches for securing an enclosure |
US20230235834A1 (en) * | 2020-04-16 | 2023-07-27 | Samson Aktiengesellschaft | Actuator for a process plant |
WO2024050284A1 (en) * | 2022-08-31 | 2024-03-07 | Dresser, Llc | Integrating fluid pathways into a valve superstructure |
Also Published As
Publication number | Publication date |
---|---|
EP3111123A1 (en) | 2017-01-04 |
CA2940542C (en) | 2022-06-14 |
CN104913101B (en) | 2019-07-19 |
SA516371739B1 (en) | 2021-02-13 |
WO2015130726A1 (en) | 2015-09-03 |
CN204878988U (en) | 2015-12-16 |
CA2940542A1 (en) | 2015-09-03 |
US20170002952A1 (en) | 2017-01-05 |
EP3111123B1 (en) | 2018-01-31 |
RU2016136694A3 (en) | 2018-09-04 |
RU2672235C2 (en) | 2018-11-12 |
US9970567B2 (en) | 2018-05-15 |
CN104913101A (en) | 2015-09-16 |
US9458947B2 (en) | 2016-10-04 |
RU2016136694A (en) | 2018-03-29 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US9970567B2 (en) | Actuator apparatus with internal tubing and anti-rotation mechanism | |
US9206909B2 (en) | Anti-rotation assemblies for use with fluid valves | |
TWI662216B (en) | Fluid controller | |
US11047483B2 (en) | Valve with self-aligning stem tip | |
US8517046B2 (en) | Redundant metal-to-metal seals for use with internal valves | |
CN103097785A (en) | Valve seat apparatus for use with fluid valves | |
US20140264138A1 (en) | Valve seat assemblies | |
CA2941692C (en) | Diaphragm actuators having adjustable actuation force | |
US8336849B2 (en) | Conical seat shut off valve | |
US20170045147A1 (en) | Seal assemblies for use with fluid valves | |
CN205504121U (en) | Clamp type valve gap subassembly and have axial -flow type control valve of this subassembly | |
EP2888395B1 (en) | Methods and apparatus to assemble actuators | |
US10215303B2 (en) | Adjustable travel stop for a piston actuator | |
US9599237B2 (en) | 3-way inline air operated valve | |
US20220349481A1 (en) | Globe Valve | |
US20150060708A1 (en) | Bellows valve with valve body cylinder adapter |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: FISHER CONTROLS INTERNATIONAL LLC, IOWA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ARNOLD, DAVID ANTHONY;ADAMS, DANIEL MARTIN;REEL/FRAME:032478/0526 Effective date: 20140224 |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
MAFP | Maintenance fee payment |
Free format text: PAYMENT OF MAINTENANCE FEE, 4TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1551); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 4 |
|
MAFP | Maintenance fee payment |
Free format text: PAYMENT OF MAINTENANCE FEE, 8TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1552); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 8 |